Apparatus for tightening threaded fasteners

ABSTRACT

According to a first aspect of the invention we provide an apparatus for coupling a shank of a threaded fastener and a torque device including: —a first coupling member having an external surface portion defined by more than two steps that forms a taper; a second coupling member having an inversely tapered internal surface portion non-rotatably engagable with the tapered external surface of the first coupling member; wherein the steps of the first coupling member and the second coupling member are shaped either as angled cylinders, frustums of an angled stepped cone or frustums of an angled curved solid; and wherein the diameters of the steps of the first coupling member and the second coupling member are less than the diameter of the shank. 
     Advantageously, this aspect of the invention allows for an increased load bearing surface area between the coupling members without increasing the overall diameter of the apparatus; a three dimensional load bearing surface area rather than a conventional two dimensional plane; more efficiently and evenly distributed load stress distribution over the load bearing surface area; higher torsion strength; and apparatus with lower mass, dimensions and volume.

CROSS REFERENCE TO RELATED APPLICATION

This Application is a divisional application of co-pending U.S.application Ser. No. 13/814,229, having Filing Date of 27 Mar. 2013,entitled “Apparatus For Tightening Threaded Fasteners”, an entire copyof which is incorporated herein by reference and from which the presentapplication claims its priority under 35 USC 119(a)-(d).

Innovations disclosed in this Application advance technology disclosedin the following commonly owned issued patents and patent applications,entire copies of which are incorporated herein by reference: U.S. Pat.No. 5,137,408, having Filing Date of Dec. 3, 1991, entitled “FasteningDevice”; U.S. Pat. No. 5,318,397, having Filing Date of May 7, 1992,entitled “Mechanical Tensioner”; U.S. Pat. No. 5,622,465, having FilingDate of Apr. 26, 1996, entitled “Lock Nut”; U.S. Pat. No. 5,640,749,having Filing Date of Jun. 13, 1995, entitled “Method Of And Device ForElongating And Relaxing A Stud”; U.S. Pat. No. 5,888,041, having FilingDate of Oct. 17, 1997, entitled “Lock Nut”; U.S. Pat. No. 6,254,322,having Filing Date of Mar. 3, 1998, entitled “Bolt With A Bolt Member, AWasher And A Sleeve For Applying Forces To The Bolt Member And TheSleeve”; et al.

DESCRIPTION OF INVENTION

Conventional threaded fasteners are known. Mechanical fastening withhelically threaded components is typically achieved with bolts, studs,screws, nuts and washers. Washers are thin members that can be placedbetween the fastener and the fastened component. Washers are typicallyused to prevent frictional damage to assembled components. Washers arealso commonly used to distribute stresses evenly and to control frictionlosses. Nuts are internally threaded fastening members commonly used toretain and or deliver load to an externally threaded fastener. Nutstypically have an external geometry that will allow rotational couplingwith a torque input device or machine.

Self-reacting nuts are typically comprised of an inner sleeve, outersleeve and washer. Self-reacting fasteners such as the HYTORC Nut usethe washer as a reaction point for the application of input torque tothe outer sleeve. In a self-reacting fastener the outer sleeve functionsas the nut while the inner sleeve becomes an extension of the stud andis rotationally coupled with the washer. This rotational couplingprevents sliding motion between the inner sleeve and stud threads duringthe application of torque to the outer sleeve. Self-reacting nuts withthe same external geometry as conventional nuts suffer from higherbearing surface stresses. The bearing surface stresses are higherbecause the outer sleeve inside diameter is increased to allow space forthe inner sleeve causing a thinner wall thickness than standard nuts.

In contrast to conventional threaded fasteners, self-reactingthree-piece mechanical tensioner fasteners such as the HYTORC NUT,include an outer sleeve, inner sleeve and washer. Self-reactingfasteners such as the HYTORC Nut use the washer as a reaction point forthe application of input torque to the outer sleeve. In a self-reactingfastener the outer sleeve functions as the nut while the inner sleevebecomes an extension of the stud and is rotationally coupled with thewasher. This rotational coupling prevents sliding motion between theinner sleeve and stud threads during the application of torque to theouter sleeve. Self-reacting nuts with the same external geometry asconventional nuts suffer from higher bearing surface stresses. Thebearing surface stresses are higher because the outer sleeve insidediameter is increased to allow space for the inner sleeve causing athinner wall thickness than standard nuts.

Additionally devices of coupling or mating a reaction or an output shaftof a torque output device to fasteners used in bolting also are known.Self-reacting three-piece mechanical tensioner fasteners typically havespline, hex or square features to allow torsion coupling with thereaction member of the torque input device. This is achieved withmachined rotational interferences between two parts. The interference istypically created with a male and female engagement between any twomating features that prevent rotation between the two parts.

Three-piece mechanical tensioning stud devices are also known. Theyconsist of a stud, nut and washer. The stud has external threads on bothends. Under the upper thread the stud will also have a spline or othergeometry to create a rotational coupling with the inner diameter of thewasher. The topside of the stud will also have a spline or othergeometry to allow rotational coupling with the reaction shaft of thetorque input device. The nut is internally threaded to mate with thethreads on the topside of stud. The nut will have a spline or othergeometry to allow the introduction of torque from torque input device.The washer has an internal geometry that will mate rotationally with thespline or other geometry under the top thread of the stud.

In bolting applications stresses are typically near the elastic limitsof the materials. The reaction feature that couples the three-piecemechanical tensioning stud to the torque of the torque input devicetypically has to be oversized to prevent elastic material failures.Therefore it is not possible with known coupling features to carry thehigh magnitude of torque with an internal feature such as a square,hexagon or internal spline hole in the top surface of the stud.Consequently prior art applications that are subject to high boltingstress must have an external feature on the topside of the stud thatwill allow the coupling of a sufficiently sized reaction shaft from thetorque input device.

The present invention has therefore been devised to address theseissues.

According to a first aspect of the invention we provide an apparatus forcoupling a shank of a threaded fastener and a torque device including:—a first coupling member having an external surface portion defined bymore than two steps that forms a taper; a second coupling member havingan inversely tapered internal surface portion non-rotatably engagablewith the tapered external surface of the first coupling member; whereinthe steps of the first coupling member and the second coupling memberare shaped either as angled cylinders, frustums of an angled steppedcone or frustums of an angled curved solid; and wherein the diameters ofthe steps of the first coupling member and the second coupling memberare less than the diameter of the shank.

Advantageously, this aspect of the invention allows for an increasedload bearing surface area between the coupling members withoutincreasing the overall diameter of the apparatus; a three dimensionalload bearing surface area rather than a conventional two dimensionalplane; more efficiently and evenly distributed load stress distributionover the load bearing surface area; higher torsion strength; andapparatus with lower mass, dimensions and volume.

Further features of the invention are set out in claims 2 to 24 appendedhereto.

The invention may be described by way of example only with reference tothe accompanying drawings, of which:

FIG. 1 is a perspective view of a threaded fastener with an embodimentof the present invention;

FIG. 2 is a side, cross-sectional view of an inner sleeve of anembodiment of the present invention;

FIG. 3 is a side, cross-sectional view of an outer sleeve of anembodiment of the present invention;

FIG. 4 is a side view of a threaded fastener for use with an embodimentof the present invention;

FIG. 5 is a side, cross-sectional view of an embodiment of the presentinvention;

FIG. 6 is a side, cross-sectional view of an embodiment of the presentinvention;

FIG. 7 is a side, cross-sectional view of an embodiment of the presentinvention;

FIG. 8 is a side, cross-sectional view of an embodiment of the presentinvention;

FIG. 9 is a side, cross-sectional view of an embodiment of the presentinvention;

FIG. 10 is a side, cross-sectional view of an embodiment of the presentinvention;

FIG. 11 is a side view of an embodiment of the present invention;

FIG. 12 is a perspective view of an embodiment of the present invention;

FIG. 13 is a cross-sectional view of an embodiment of the presentinvention;

FIG. 14 is a perspective view of an embodiment of the present invention;

FIG. 15 is a perspective view of an embodiment of the present invention;

FIG. 16 is a perspective view of an embodiment of the present invention;and

FIG. 17 is a perspective view of an embodiment of the present invention.

Referring to FIGS. 1-4 by way of example, this shows an apparatus 1—astepped conical fastener assembly—in accordance with an embodiment ofthe present invention. Apparatus 1 has an inner sleeve member 100 and anouter sleeve member 200 and is used with, by way of example, a threadedstud 300. Inner sleeve member 100 is rotatably and threadedly engagablewith stud 300; rotatably and taperedly engagable with outer sleevemember 200; and non-rotatably engagable with an action portion of atorque input device. Outer sleeve member 200 is non-rotatably engagablewith a reaction portion of the torque input device; and rotatably andtaperedly engagable with inner sleeve member 100. Inner sleeve member100, when rotated by the action portion of the torque input device,applies a load to stud 300 to close a joint (not shown).

Inner sleeve member 100 is an annular body and, as shown in FIGS. 1 and2, formed as a sleeve. It has an inner surface 110 with an inner helicalthread means 120 engagable with an outer surface 310 with an outerhelical thread means 320 of stud 300. It has an outer surface 111 with acylindrical formation 121 which is rotatably engagable with an innersurface 210 with a cylindrical formation 220 of outer sleeve member 200.It further has a lower surface 113 which is rotatably engagable withinner surface 210.

Cylindrical formation 121 is shaped as an inverted frustum of a steppedcone which has a tapered or conical appearance from the bottom up. Eachstep on outer surface 111 is progressively smaller from top to bottom.An external hollow cylindrical feature is removed from the outside ofinner sleeve member 100 at a shallow depth. Successive external hollowcylindrical features are removed at regular length and width intervals.Each successive feature starts where the preceding feature stops. Thegeometric pattern of removed external cylindrical features continuesuntil space restricts the addition of another internal cylindricalfeature.

Inner sleeve member 100 further has an upper surface 112 with a couplingmeans 130 which may be formed by a plurality of bores extending in anaxial direction and spaced from one another in a circumferentialdirection. Coupling means 130 non-rotatably engages with the actionportion of the torque input device.

Outer sleeve member 200 is an annular body and, as shown in FIG. 3,formed as a sleeve. It has inner surface 210 with cylindrical formation220 which is rotatably engagable with an outer surface 111 withcylindrical formation 121 of inner sleeve member 100. Outer sleevemember 200 has an outer surface 211 with a coupling means 230. Couplingmeans 230 is formed by a plurality of outer spines extending in an axialdirection and spaced from one another in a circumferential direction.Coupling means 230 non-rotatably engages with inner spines of a reactionportion of the torque input device.

Cylindrical formation 220 is shaped as a frustum of a stepped cone whichhas a tapered or conical appearance from the top down. Each step oninner surface 210 is progressively smaller from top to bottom. Aninternal cylindrical feature is removed from the inside of outer sleevemember 200 at a shallow depth. Successive internal cylindrical featuresare removed at regular length and width intervals. Each successivefeature starts where the preceding feature stops. The geometric patternof removed internal cylindrical features continues until space restrictsthe addition of another internal cylindrical feature.

Stud 300 has a cylindrical shape with outer helical thread means 320 formating with inner helical thread means 120 of inner sleeve 100. An end312 of stud 300 has a coupling means 314 which may be formed by apolygonal formation 330, which in this case is a hexagon shape.Polygonal formation 330 allows for rotational coupling with the torqueinput device.

Second coupling member 150 further has a lower surface 163 which restson an upper surface of the joint. Lower surface 163 may be substantiallyrough and may be made in many different ways, for example by a pluralityof ridges, ripples or teeth.

The stepped conical fastener geometry of apparatus 1 creates tensileload in stud 300 by the mechanical sliding action through the helicalinclined plane between stud threads 320 and inner sleeve member threads120. The sliding helical thread action is created by using the torqueinput device to apply rotation under torque to inner sleeve membercoupling means 130 while reacting the torque on outer sleeve memberexternal splines 230. As outer surface 111 and inner surface 210 aresubstantially smooth, outer sleeve member 200 remains static while innersleeve member 200 rotates. The reaction element of the torque inputdevice is rotationally coupled with end 312 of stud 300 by couplingmeans 314. This prevents rotation of stud 300 and allows the relativesliding action between inner sleeve member threads 120 and studs threads320. Stud translation occurs in proportion to the resistance againstsuch translation as the torque input device continually applies torqueto inner sleeve member 100 while reacting on outer sleeve memberexternal splines 230 and being rotationally coupled with stud 300 bycoupling means 314.

Inner sleeve member coupling means 130 may be formed by any suitablegeometry or used with other means or features for rotationally couplingwith the torque input device such as gear teeth, hex, double hex,castellation or any other common geometry that allows rotationalcoupling. One possible alternative is hex geometry shown in FIG. 5 as530.

Outer sleeve member coupling means 221 may be formed by any suitablegeometry or used with other means or features for rotationally couplingwith the torque input device such as gear teeth, hex, double hex,castellation or any other common geometry that allows rotationalcoupling. One possible alternative is hex geometry shown in FIG. 6 as621.

Note that the quantity, dimensions, geometries and intervals of removedexternal (inner sleeve member 100) and internal (outer sleeve member200) cylindrical features may vary to optimize characteristics ofapparatus 1, such as, for example, stress biasing, depending on theapplication.

FIG. 2 shows inner sleeve member 100 with four external cylindricalfeatures removed at regular length and width intervals. FIG. 3 showsouter sleeve member 200 with four internal cylindrical features removedat regular length and width intervals. As shown in FIG. 7, varying thequantity, dimensions, geometries and intervals from one removed externaland internal cylindrical feature to the next varies the nominal angles,step heights and step widths of an outer surface 711 with a cylindricalformation 721 and an inner surface 710 with a cylindrical formation 720.Alternatively, the step length may be sized infinitely small to create anearly smooth taper. External portions of inner sleeve member 100 andinternal portion of outer sleeve member 200 may be removed in one stepto form smooth conical surfaces, respectively.

FIG. 8 shows an outer surface 811 with a cylindrical formation 821 andan inner surface 810 with a cylindrical formation 820 with mating facesof varying vertical spacing, or step heights. This allows movement onselective steps only as other steps are loaded. Plastic deformationallows vertical movement therefore strategically biasing stressdistribution across each stepped face. In other words, increasedclearance or spacing between mating faces of inner and outer sleevemembers 100 and 200 allow for radial expansion during loading.

FIG. 9 shows an outer surface 911 with a cylindrical formation 921 andan inner surface 910 with a cylindrical formation 920 with mating facesof varying step face angles. This promotes more evenly and controlledbiasing stress distribution across the steps. In other words, either orboth inner and outer sleeve members 100 and 200 may have steppedvertical surfaces with varying pitch angles to bias stress to selectivehorizontal stepped surfaces.

FIG. 10 shows outer sleeve member 200 having internal features at bottomthat couple with similar mating external features added to stud 300.These may include splines, knurls, hex, slots, double hex or othergeometry. They allow axial translation of stud 300 but couple rotationalmovement of outer sleeve member 200 and stud 300. Both coupling means314 formed of polygonal formation 330 and the necessity to couple thishex with the reaction member of the torque input device are no longernecessary. Internal spline 1040 and mating external spline 1041 form aspline interface between outer sleeve member 200 and stud 300,respectively.

In standard bolting industry terms, apparatus 1 includes a nut (innersleeve member 100) and a washer (outer sleeve member 200). The standardbolting flat surface nut and washer interface is changed. The torquereaction point is moved upwards, as compared to conventional three-piecefasteners. Apparatus of the present invention utilize the concept ofconventional three-piece fasteners, which allows for surfaceconditioning of the outer sleeve to prevent galling, leveraged with aconventional nut and washer arrangement, which retains radial strainsuch that the inner sleeve may be surface conditioned with minimal riskof fracture.

Advantageously, the invention allows for an increased load bearingsurface area between the inner sleeve member, which is clamped, and theouter sleeve members without increasing the overall diameter of theapparatus; a three dimensional load bearing surface area rather than aconventional two dimensional plane; more efficiently and evenlydistributed load stress distribution over the load bearing surface area;higher torsion strength; and apparatus with lower mass, dimensions andvolume.

Referring to FIGS. 11-14 by way of example, this shows an apparatus 1101for torsionally coupling a threaded fastener 1110 and a torque inputdevice 1102 in accordance with an embodiment of the present invention.Apparatus 1101 has a first coupling member 1103 with a tapered externalsurface 1104 and a polygonal formation 1105; and a second couplingmember 1113 having an inversely tapered internal surface 1114 and apolygonal formation 1115 non-rotatably engagable with tapered externalsurface 1104 of first coupling member 1103.

In other words, apparatus 1101 torsionally couples torque input device1102 and threaded fastener 1110 of the kind having a shank 1111 with atapered axial bore 1112 at one end. Apparatus 1101 includes couplingmember 1103 having inversely tapered external surface 1104 non-rotatablyengagable with tapered axial bore 1112.

Discussion related to quantity, dimensions, geometries and intervals ofremoved external (inner sleeve member 100) and internal (outer sleevemember 200) cylindrical features of FIGS. 1-10 generally applies to thequantity, dimensions, geometries and intervals of removed external(first coupling member 1103) and internal (second sleeve member 1113)polygonal features of FIGS. 11-14. Note that the interface between innerand outer sleeve members 100 and 200 is cylindrical and smooth thusallowing relative rotation. Note, however, that the interface betweenfirst and second coupling members is polygonal and angled thus norelative rotation is possible.

A conical geometry for torsional coupling of a threaded fastener and atorque output device yields a better load stress distribution. Theembodiment of FIGS. 11-14 introduces a low profile coupling geometrythat will allow a torsion-coupling feature on the top of a stud to beformed internally. This distributes stresses more evenly and thereforeallows for a more efficient packaging of the coupling features.

Generally, a stepped 12-point hole in the top surface of the stud isused for torsion coupling with a three-piece mechanical stud-tensioningdevice and/or an apparatus for use with the stud. An internal 12-pointfeature is placed in the top of the stud at a shallow depth. Successive12-point features are progressively added at smaller 12-point sizes eachat shallow depths and each starting where the preceding 12-pointstopped. The pattern of decreasing 12-point geometry will decrease untilspace restricts the addition of another 12 point. Advantageously, ashaft of the torque input device with external matching features foreach of the steps will allow for evenly distributed stress distributionand high torsion strength while decreasing the mass and volume of thestuds.

As shown in FIGS. 16 and 17, varying the depth and size change from one12-point feature to the next will increase or decrease the nominal angleof the conical shape these features form. The 12-point feature can besubstituted with any geometry that will prevent rotation between the twoparts, such as the hex in FIG. 15. Additionally, the step depth can besized infinitely small to create a smooth taper. Mixed step sizes andgeometries can be used to optimize production of such a coupling.

Note that any type of suitable components, sizes and materials ofapparatus of the present invention may be used, including: fastenercategories, for example wood screws, machine screws, thread cuttingmachine screws, sheet metal screws, self drilling SMS, hex bolts,carriage bolts, lag bolts, socket screws, set screws, j-bolts, shoulderbolts, sex screws, mating screws, hanger bolts, etc.; head styles, forexample flat, oval, pan, truss, round, hex, hex washer, slotted hexwasher, socket cap, button, etc.; drive types, for example phillips andfrearson, slotted, combination, socket, hex, allen, square, torx,multiple other geometries, etc.; nut types, for example hex, jam, cap,acorn, flange, square, torque lock, slotted, castle, etc.; washer types,for example flat, fender, finishing, square, dock, etc.; and threadtypes, for example sharp V, American national, unified, metric, square,ACME, whitworth standard, knuckle, buttress, single, double, triple,double square, triple ACME, etc.

It will be understood that each of the elements described above, or twoor more together, may also find a useful application in other types ofconstructions differing from the types described above. The featuresdisclosed in the foregoing description, or the following claims, or theaccompanying drawings, expressed in their specific forms or in terms ofa means for performing the disclosed function, or a method or processfor attaining the disclosed result, as appropriate, may, separately, orin any combination of such features, be utilized for realizing theinvention in diverse forms thereof.

While the invention has been illustrated and described as embodied in afluid operated tool, it is not intended to be limited to the detailsshown, since various modifications and structural changes may be madewithout departing in any way from the spirit of the present invention.

Without further analysis, the foregoing will so fully reveal the gist ofthe present invention that others can, by applying current knowledge,readily adapt it for various applications without omitting featuresthat, from the standpoint of prior art, fairly constitute essentialcharacteristics of the generic or specific aspects of this invention.

When used in this specification and claims, the terms “tapered”,“taperedly” and variations thereof mean that the specified features,steps, quantities, dimensions, geometries and intervals may, from oneend to another, either gradually, suddenly, step-wisely, and/orconically: be inconsistent, vary, narrow, diminish, decrease, getsmaller, thin out, etc.

When used in this specification and claims, the terms “comprising”,“including”, “having” and variations thereof mean that the specifiedfeatures, steps or integers are included. The terms are not to beinterpreted to exclude the presence of other features, steps orcomponents.

What is claimed is:
 1. An apparatus for coupling a shank of a threadedfastener and a torque device including:— a first coupling member havingan external surface portion defined by more than two steps that forms ataper; a second coupling member having an inversely tapered internalsurface portion non-rotatably engagable with the tapered externalsurface of the first coupling member; wherein the steps of the firstcoupling member and the second coupling member are shaped either asangled cylinders, frustums of an angled stepped cone or frustums of anangled curved solid; and wherein the diameters of the steps of the firstcoupling member and the second coupling member are less than thediameter of the shank.
 2. An apparatus according to claim 1 wherein thesteps of the first coupling member and the second coupling member areshaped as solids not limited to particular step quantities, dimensions,geometries, angles and/or intervals.
 3. An apparatus according to claim1 wherein the internal surface portion of the second coupling membersubstantially surrounds the external surface portion of the firstcoupling member.
 4. An apparatus according to claim 1 wherein the firstcoupling member is non-rotatably engagable with an action portion of thetorque device.
 5. An apparatus according to claim 1 wherein the secondcoupling member, when rotated by an action portion of the torque device,applies a load to the threaded fastener.
 6. An apparatus according toclaim 1 wherein the first coupling member is formed on a reaction shaftof the torque device and wherein the second coupling member is formed onthe shank of the threaded fastener.
 7. An apparatus according to claim 6wherein the first coupling member is formed as an axial protrusion andwherein the second coupling member is formed as an axial bore.
 8. Anapparatus according to claim 1 wherein the first coupling member isformed on a shank of the threaded fastener and wherein the secondcoupling member is formed on a reaction shaft of the torque device. 9.An apparatus according to claim 8 wherein the first coupling member isformed as an axial bore and wherein the second coupling member is formedas an axial protrusion.
 10. An apparatus according to claim 1 having aninfinite number of steps such that the external surface portion of thefirst coupling member is smoothly tapered and the inversely taperedinternal surface portion of the second coupling member is smoothlytapered.
 11. A system for fastening objects including a combination of atorque power tool either pneumatically, electrically, hydraulically ormanually driven and a threaded fastener having an apparatus according toeither claim 1-10.